Tens transfer mechanism



June 7, 1949. E. P. DRAKE 2,472,696

TENS TRANSFER MECHANISM Filed March 13, 1945 4 Sheets-Sheet l INVEN TOR. [am/e0 A DQAKE ATTOPA/[Y' June 7, 1949. E. PQDRAKE TENS TRANSFER MECHANISM 4 Sheets-Sheet 2 Filed March 15, 1945 IN VENTOR. fawn/. 0 P 02mm:

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June 7, 1949. E. P. DRAKE TENS TRANSFER MECHANISM 4 Sheets-Sheet 5 Filed March 13, 1945 m m m m [an 420 f. 024k:

ATTOP/VZY June 7, 1949. P, DRAKE 2,472,696

" TENS TRANSFER MECHANISM 4 Sheets-Sheet 4 Filed March 13, l-945 INVENTOR. fan A20 P 0mm- ATTOP/VfY Patented June 7, 1949 UNITED STATES PATENT OFFICE TENS TRANSFER MECHANISM Edward P. Drake, Glendale, Calif assignor to Clary Multiplier Corporation, Los Ang'eles, Calif., a corporation of California Application March 13, 1945, Serial -N05582554 9 Claims.

1 The present invention relates to calculating machines, and has particular reference to machines of the type disclosed in the copending-application of Robert Boyden, Serial No.-582,'553 filed March 13, 1945. Reference may .be had to said application for a disclosure of a complete calculating machine in which the embodiment of the present invention may be incorporated. However, it is to he understood that the invention is not limited to a machine of the above type but may be incorporated in any machine or device wherein it is desired .to accumulate values.

One object of the present invention is to provide .a simple and improved accumulator and tens transfer mechanism which is absolutely reliable at high speeds.

Another object is to provide a two directional accumulator capable of high speed operation.

Another object is to positively prevent overthrow and/or rebound of-an accumulator element during a tens transferoperation.

Another object is to provide a tens transfer mechanism in which the conditioning and determination of the direction of a tens transfer operation is effected-directly by an accumulator element.

Another object is to reduce the force required to condition a tens transfer device to effect a'tens transfer.

The manner in which the above and other objects of the invention are accomplished will be readily understood on reference to the following specification read in conjunction with the accompanying drawings wherein;

Fig. l is a transverse sectional View through an accumulator embodying the present invention, with the transfer pawl in a neutral condition, and is taken along the line 1-4 of Fig. 4.

Fig. 2 is a transverse sectional view, similar to that of Fig. .1, but showing the transfer pawl in a subtract condition.

Fig. '3 is a transverse-sectional view similar to Figs. 1 and '2, but taken along the line of 3-3 of Fig. 4 and illustrating the transfer pawl at the end of its stroke.

Fig. 4 is a front view of several orders of the accumulator.

Fig. 5 is a longitudinal sectional view through the control section of an adding machine embodying the accumulator of the present invention.

Fig. 6 is a longitudinal sectional view through the adding machine, illustrating the key boar and one of the drive racks.

at the accumulated value.

.Fig. 'I is "a side view-of thegear train for transmitting rotation to the tens transfer shaft.

The machine in which the preferred embodiment of the invention is illustrated is of the adding machine type and includes a full keyboard comprising a series of rows of amount keys as more fully disclosed in said Boyden application. Each row comprises nine keys ranging in value from 1 to 9, certain of which are illustrated at 9 in Fig. 6.

Each key 9, when depressed, serves as a stop to limit the movement of an aligned drive rack 19 which drives the accumulator to enter therein a value corresponding to the value of the depressed aligned key and to set the printing mechanism to print the said value. The racks are guided for longitudinal movement at the rear thereof by a stationary rod 8l,-embraced by slots 82! formed in the racks, there being asuitable sup- .port (not shown) for likewise guiding the forward ends of the racks.

Each rack .is provided with equally spaced shoulders 19, the spacings of which are slightly larger than the spacings of the keys 9 so that each rack, when yieldably advanced toward the front .of the machine will strike the key stem of a depressed key after it has moved forward a number of increments equal to the value of the depressed key. Also formed on each rack I9 is a pair of rack gear sections 83 and 84 located on opposite sides of an associated accumulator gear 85 rotatably mounted on an accumulator shaft 86 forming part of the accumulator unit.

A plurality of control keys or bars, some of which are illustrated in Fig. 5, are provided to cause the machine to perform different functions. For example, asubtract :bar 13 is provided, which when depressed, causes the machine to subtract an amount set up on the keys 9 from an amount entered in the accumulator which will be described presently. A non-add bar I4 is provided which, when depressed, causes the machine to print a value (in a manner not shown) without entering the same in the accumulator. A subtotal 'bar [8 is provided to cause the accumulator to be returned to zero value for the purpose of registering the racks and printer at the total value previously accumulated in the accumulator so as to print such value and to then return the accumulator to its previous accumulated value. A total bar I! is provided to return the accumulator to zero so as to register the racks and printer In this case the accumulator is allowed to remain in its zero position after the printing operation.

The accumulator is of the two directional subsequent transfer type capable of receiving both additions and subtractions.

Referring to Figs. 1 to 4, inclusive, the accumulator shown therein is arranged to be raised or lowered for the purpose of engaging the various accumulator gears 85 with either the upper rack gear sections 83 or the lower rack gear sections 88 (Fig. 6) of the racks I9 in accordance with the type of problem to be performed. During an additive operation, the accumulator is raised to mesh the gears 85 with the upper rack gear sections 89 whereby the gears will be rotated in a counter-clockwise direction during the subsequent forward movements of the racks I9, while, during a subtractive operation, the accumulator is lowered to mesh the gears 85 with the lower rack gear sections 84 so that the subsequent forward rack movement will drive the gears in a clockwise direction.

The accumulator comprises in general the hereinbefore mentioned accumulator shaft 88 and a second shaft 81, both rotatably mounted in bearings formed in a series of ordinarily spaced brace plates it (see Fig. 4. in particular) rigidly held in spaced relation with each other by suitable interlocking combs I I well known in the art. A rod I2 is passed through the various plates I9 adjacent each comb to hold the latter in looking position.

The shafts 86 and 87 are guided for vertical movement in vertically extending slots, one which is shown at I3, (Fig; 5) formed in side plates Eta of the machine and thus carry the various brace plates I8 and tens transfer mechanism comprising the accumulator unit.

For the purpose of raising and lowering the accumulator unit in accordance with the type of problem being performed, there is provided a box cam 94 (Fig. 5) pivoted on a stationary frame stud 95 and having a cam groove 98 therein embracing a roller 91 rotatably mounted on the shaft 86 at the left hand endthereof. Clockwise rocking movement of the cam 94 beyond its central illustrated position will raise the accumulator into its adding position while counter-clockwise rocking of the cam will lower the accumulator into its subtractive position. Suitable means, such as a shaft 99 rotatably mounted in the side frames of the machine and having arms (not shown) attached at opposite ends thereof and embracing the shaft 86 as illustrated in said Boyden application are preferably provided to insure parallel movement of the accumulator in its vertical travel.

The above noted meshing operation is performed in addition and substraction operations in advance of each forward stroke of the racks I 9 so that, as the racks I9 are driven forward, the gears 85 will be rotated a number of increments determined by the extent of travel of the corresponding racks, and since there are ten teeth in each gear, each tooth advance of the gear will represent one digit entered into the particular order of the accumulator in which said gear is located. At the end of the forward travel of the racks in addition, subtraction and totaling operations the gears 85 will be demeshed from the gear rack sections and located in their neutral positions illustrated in Fig. 6 to permit the return of the racks without affecting the accumulator.

As each gear 85 moves through one revolution or ten tooth spaces as a result of accumulating ten digits it conditions a transfer mechanism to subsequently enter one digit into the gear 85 of the next arithmetically higher order to the left. For this purpose, a transfer pawl I5 is provided, being capable of rotating its associated gear an increment of one tooth space in either direction.

Each pawl I5 surrounds its associated gear and is pivoted on one side of the gear 85 at 511 on a cam follower lever I 6 pivotally supported on the lower shaft 87. Lever I9 is provided with a roller I611 adapted to be engaged and moved by an aligned one of a series of transfer cams I8 to be described in detail hereinafter.

Pawl I5 is provided with three detents H, the central one of which is normally engaged by the roller II9a of a centralizer lever II9 pivoted on a brace plate stud 28 attached to the associated brace plate I8 and pressed against the pawl by a spring 2! extending between the centralizer and a stud 22, also attached to the brace plate I 8. In addition to holding the pawl I5 in any of three positions, the centralizer II 9 also normally maintains the pawl in a rearward position as illustrated in Figs. 1 and 2 wherein the lever I6 rests against the adjacent comb retaining rod I2, and is capable of returning the pawl from its forward position illustrated in Fig. 3 after the associated cam I8 is removed from contact with the roller of the associated lever I8.

Each gear 85, as it rotates in a clockwise direction from its Zero position illustrated in Fig. 1 to its 9 position illustrated in Fig. 2 during a subtraction operation, carries a tooth 23 attached integrally thereto into engagement with an ear 2d located on the pawl I5 on the side of the gear 85 opposite the side thereof at which the pivot II5a is located. The tooth 23 thus rocks the pawl I5 upwardly about its pivotal support 5a. Substantially halfway through its upward movement, the roller I I9a on the centralizer I I9 moves over the tip 25 on the transfer pawl located between the central and lower detents Ill. The spring 2i thus becomes effective to cause the centralizer to tend to exert a camming force on the pawl so as to move it further into its fully conditioned position illustrated in Fig. 2. However, at normal speeds the tooth 23 supersedes such force and maintains contact with the car 24 until such tooth reaches substantially its position illustrated in Fig. 2. From there on, the momentum of the pawl and the camming effect of the centralizer carry it to its fully conditioned position. In view of the longer radius of the arc of travel of the ear 24 the latter will gradually move outward relative to the tooth 23 so that as it reaches its fully conditioned position it will be entirely clear of the tooth, permitting the latter to continue its rotational movement without interference with the tooth. In view of this construction wherein the tooth 23 exerts a force on the pawl I5 throughout its total rotative travel between nine and zero registration it will be seen that such required force may be reduced to a minimum and the shock and strain upon the various parts of the accumulator likewise reduced. In the fully conditioned position of the pawl I5, 9, transfer tooth I5a thereon is located directly behind a tooth 26 of the gear 85 so that in a subsequent transfer phase of the operation in which the cam follower arms I8 are rocked by the cams I8 to advance the pawls E5, the tooth I5a will engage and drive the gear 85 one tooth space in a clockwise or subtractive direction.

Likewise, during an additive operation and when an accumulator gear 85 rotates counterclockwise from a 9 position to a 0 position the tooth 23 thereof will strike the ear 24 of the associate tra sfer oa l i, toolto; l tter into a lower n sltloh mot shown). to whteh ro ler two o the associated -.eehtte 1her no th ses the up er leteot Ill these Bowl !5 s mme rica exac ly t esehte action will other as in a suotraotlre oonslttlohlhe .o eret oh erreeht tha the sear 8 will e rotated the tooth to e Q l lW GIQ KWEQ or additive dtl'eetloh- That as e awl. it s. owered eeth .2 the eon ll be lo ated p site a teeth so. the seer-so that when he pawl is. so e eolleotls lher el. or ard the tooth 28 w ll aelt'ahee the eeeleooe teeth s ace.-

lt w l he hotetl hat o rlhs esldltlte, stlhtraelve ahtl otellh e eretlehe th aeethhtlletor wil b el heaee l he the reehstl, er i ll he ret rned to its hehtral .hosltloh are shown he hea rior o the transter nhese wh eh. occur et th Therefore, the end o the d git n Phase o the ole the ho s is 1. a he o d s hioh ee tve a r nser w l be oend t oned orle atesl uppe o o er p s t n d pending on th ty e or] op ral h an h sea s will, he eomhlete y mesh m he ree s- Me n e ro ded to elteetl s e tens sf r n he ar ous orrlers ot th roaohlne bee-v nin a the hear to he lowermo t o righ a order hen t wlh the eooll hhle or from e n s in ig For ur ose, a t ansr shaft t i 'e a ahlr hl lt ed in th side plates o h m chi e n a meoher no shown a d a u ted the on the various transfer cams [8. The cams [8 are held in spaced relattion with each other by sleeves 3114;, It will be o ed n e enc t Fig and 2 that the vari o cams 8 a e ar anged ahelteal .r w about the shaft 30 a r the Pu ose or faoil t hne assembly n anufaetll e o the various t ns fe cam l8, nd to enabl in rchangeabil ty of t e, t ey ar all mad identi al with sym metrical contours and each is provided with an octa on n ng adapted to e itted v r the square e t r t e shat 30-. Al o, a rl e h u h two iametr ally enhse l point to the n ng or eac am l ir'lg. ellleoent the ,of sym e r x e d v 2 /2 degrees item sold o hat by ppr ria ely fitting theams ov th shaft h ma e arahs cl at .3 /2 deg ee rom each other,

It will be noted that; the. eehtrellzers Us and e levers 6 tone shb teht 'allh er llel not; a rehgements. to ca y the. naw s l5 through paths which closely appr ximate a straight line ee l of the ang a ooholtloo h Pos i n r" he pa l ab ut it pi t Hie Dur ng n le ran e r ke 1.. ewheh. a pawl is not eondi n d t a tran r, the lat er w ll trav thr u h ts s ro wi hou engag n th ear 85 but d ring a. t nsfer s rehe lh. which t e pa l as b en condi ioned to e l e-e trans er on or he o her of e eeth li e an not. the paw i dr aid e a Purine htlr lhe mov men Whichever to h i hi 8 the gea .8 w l e en a ed by a sheoe tlhlg teeth th sear 5 a Will be raduall sh tte l. ther hy lhto t neutra p sition s th t egardless ot wh th r a suba l e or addit v treoster helhs; lhecle the pawl w l alwa s ome to est-in heotrel Postt h lust ates in h s: For exarhh et thlr o a. h ae rans er operation: and s he tooth a of paw It, drives the see; too h 2.6. the su eeeellhe ea te th?! wil eeh the t eth 25 dowhwardlr hto hetttrel, hestttoh eahhnthe. eo toh. will he eoheltletetl. l st the sear oo h 26. reaches its new ooslt oo- It, wil also. lee noted that the owl eeth 5ll...& .1 25 hit? so seated hat as h oth earns th pawl lowhwerd toward i s neutr l position, the. u per teeth 23 oll s ear te h 2 and hehind the eeeedlrle ooth ea thereby posit vely let-ev nt n ove thro of the sear; Furth rmo rebound o t e g ar rom ts advanced hosl oh will als be o eveh d hr e at he earl or the stroke o he awl both teeth 15a and. l will. lee oe teo beh nd the ad c n gear te th 2 and 3;. res cti ely! as s ow h the 3-.

A. yl'e elahl eh ra zer wl 32!! is orotte eel. to ho aeh ge r n egisterel os tion.. shown n. lee 3 a d e e awl 3. oted he braee st d 2 in juxta osi ion wtththe associated ee ll e H and. is held rrehgesemeet w th th g ar ee y a shr e 32o terrio ed b tw en, th p wl an th stu Z Meeh are p v ed f rotat n the trehster sha t 39 duri he. a t r a t o the m chine e ol an aft t d gi in ha e has een o mp e e s l u t at i F e- 7 e muti ated gear I26 and a disc 1 21 are keyed in juxtaposition ith ea h other on a cy l o able shet 5 form n h ma he s a of the maeh he- The disc I21 has a depression I28 formed in the edge thereon in alignment with the teeth or the sea 12 The r .6 i ada te o esh wi h a d ion I29 rotatably mo n ed on arre he stud I30 and having its width extending aeross both the gear I26 and the disclZ'I. The portion ot he ni H9 n a m n with. e s a 25 is jolly toothed, while the portion thereof which is in alignment with the disc 12'! has a pair 915 adjacent teeth cut w to or a bea ing surface [3| against which the periphery of the disc I21 normally rides, whereby to prevent rotation of the pinion whenever the teeth of the gear I26 are out of mesh with the teeth of the pinion. Therefore, at approximately 3/ of the revolt;- tion of the shaft 5! in the direction or arrow A, the disc will merely ride against the bearing surface l g-fl of the pinion until the teeth of the gear 126. mesh with the full toothed portion of the pinion 129 at which time the depression I28 will be aligned with the pinion teeth, permitting rota.- tion of the latter. Pinion 129 is arranged to r ve t e ra s shaft 30 u h an dler I32 iou h lleel en a r m d 3 nd eshing with a pinion I34 fixed to the shaft 30.. The length of the toothed portion of gear I25 is such that the shaft 3i) will be rotated one complete revoltition, and will come to rest in its normal position shown in s 1 an I wil be h ted th h shaft 0 s tated n oloeh l e on so hat t r hsrer am 18. lo at d in t e un s r ft-hand r e (as viewed l be he fi st t effect th tran e st ke o its. assoc t ansfe pawl l5.- Th cam r o s a e eularly that. one earn will effect a transfer stroke of its associated transfer pawl before the next adjacent hi her o er cam will ca se its t nsfer awl o 2. 0?-

s de ri oed h r ih e e var us QQhtlQl hare, including bars l3, l l1 and [8 (Fig. 5) are pro.- vitleel or controlling nd ect n o eration in the machine, depression of each'or these pars o us e r ta on of the shaft 51 o e. eor hl revo u ion s more l y closed in the elore said o oeh p c t on- Th abo con r l ba s. also ca se isins ah lower n or the eeu h lat to m sh se rs he with e her the p er eels. sear. seettoh l on the opposite sides of the pivot 95. These pins are adapted to be selectively engaged by a hook member 259 pivoted to a three armed cam follower 269 which is pivoted on the rod 8|. The cam follower 260 is urged counter-clockwise by {a spring 26! connected between one arm of the cam follower and a frame pin 262 to press a roller 263 on another arm thereof against a cam 264 keyed on the cyclic drive shaft i. Cam 264 has a high portion extending over substantially one half of its periphery whereby to rock the cam follower 289 and thereby drive and hold the hook member 259 rearward during approximately the first half of a machine cycle. Normally, during additive operations or when the machine is at rest, the hook member 259 is raised by a tension spring 2523 whereby a slot 2% therein embraces the upper pin '35? so that upon rotation of the shaft ill under control of an add bar or other control bar (not shown) the hook is moved rearward and it will rock the cam 9d clockwise to raise the accumulator into its additive position.

For the purpose of locating the hook 259 in a lowermost or intermediate position, a control bar 2611s provided, being supported for longitudinal movement by a pair of parallel links 268 pivotally suspended from the frame by pins 269. The bar 261 has four c amming surfaces 219 thereon underlying pins 232 carried by links 233 pivoted on frame pins 23%. Pins 232 underlie the stems of the control bars l3, it, it and i3 and are urged upwardly by springs extending between the pins and frame studs 2% to normally hold the control bars in raised positions.

The bar 26'! is connected by a pin and slot connection 215 to a bellcrank 2'32 pivoted on a frame stud 213 and having a pin 219 at the opposite ends thereof embraced by a slot Zita formed in the hook 2'59.

The camming surfaces 2w of the bar 261 are so arranged that upon depression of the minus bar It, the total bar i8 or the sub-total bar ll, the control bar 255? will be moved forwardly its fullest extent which, through the bellcrank 212 will lower the hook member 259 to cause a slot 275 therein to embrace the pin 258 on cam 94 so that subsequent rearward movement of the hook member 259 will place the accumulator in its lower subtractive position. The contour of the camming surface Elli underlying the nonadd bar M is such that depression of this bar will move the bar 26? and hook member 259 into their'neutral positions wherein both slots 266 and 215 of the hook member 259 will be out of registry with the pins 25'! and 258 of the cam 94.

Consequently, during the subsequent rearward movement of the hook members 259 the cam 94 will remain in its neutral position as illustrated in Fig. 5 and, therefore, the accumulator will not .be actuated during the subsequent forward movement of the racks l 9. k In order to normally maintain the cam 94 in" its neutral position when it is so placed, a centralizer 275 is provided, being pivoted on a frame stud 21'! and urged in a clockwise direction by the lower periphery of the box 'cam 94. The remainder of the lower periphery of the box cam is arranged concentric about the frame stud 95 so that the centralizer roller will eifect only a frictional force against the cam as it is moved on either side of its neutral position.

In totaling operations, the accumulator is returned in a subtractive direction to zero during the first part of the operating cycle and is then placed in its neutral position in the same manher as in addition and subtraction operations, while in sub-totaling operations, the accumulator is first returned to zero during the first part of the cycle and is then again-reset at its former accumulative valueduring the latter half of the cycle. Therefore, it is necessary in the latter operation to maintain the accumulator in mesh with the drive racks l9 until the latter have returned to their rearward positions illustrated in Fig. 6. To this end, a second cam I219 is mounted on the shaft 5| in juxtaposition with the cam 264 and is provided with a high portion extending around the major portion of the periphery thereof. The cam engages a roller 289, normally aligned with the roller 263, and carried by a second cam follower 28! also pivoted on the rod 8! and urged counter-clockwise by a spring Zilla. A slot 282 is formed in the rearwardly extending arm of the bellcrank 28L which slot is coextensive with the slot 283 formed in cam follower its. However, it will be noted that the rearwardly extending arm of the bellcrank 28! is somewhat shorter than the similar extension of the cam follower 260.

A pin 294 carried by a link 295 slides within one or both of the slots 292 and 283 depending on its position longitudinally of the machine. The link 285 is connected at its forward end to the lower arm of the bellcrank 233a which is associated with the sub-total bar [8 and is so arranged that when the bar 18 is in a raised position as indicated in Fig. .5 the pin 294 will be located solely within the slot 293 of the cam follower 269. However, upon depression of the bar It the pin 284 will be moved forwardly to locate within both the slots 282 and 283. In this condition, i. e. during a subtotaling operation, the two members 269 and 23! will move as a unit and the cam i219 will therefore, through the hook 259 hold the accumulator engaged with the drive racks l9 throughout the major portion of the cycle.

Referring to Figs. 1 to 4, a series of ordinarily spaced zero stop levers 59 are keyed to the shaft 81 adjacent the various gears 85 and are, during totaling and sub-totaling operations, rocked counter-clockwise by the shaft 81 into blocking positions relative to ears 5! formed integral with the accumulator gears 85. Thus, when the gears 85 are rotated subtractively in a clockwise direction by the drive racks l9 they will return to zero positions indicated in Fig. 1 at which time the zero locating ear 5! of each gear will be blocked by a lug 59a of its associated zero stop lever 59, thereby also stopping its associated rack l9.

The shaft 81 and zero stop levers 59 are rocked counter-clockwise by power under control of the total bar I! and sub-total bar 19 and in order to accomplish this an arm 288 (Fig. 5) is keyed to the shaft 91 and has a pin 289 thereon embraced by a slot 289a in a floating lever 299 which normally rides on the stationary frame pin 217. The

its ends.-- The link-293 is pivotally connected at thereof to the pins 232 underlying the stems of the control bars I! and I8.

noon depression of either or these two control bars the link 29! will be lowered Su fliciently to rock the lever 290 counter-clockwise about the stationary pin 2'" to position a hook 294 thereon in the path of a pm 295 carried by the cam follower 28! so that as the latter is rocked counter clockwise at the beginning of total or sub-total operations as explained herein above, the pin 295 will force the lever 290 forwardly, rocking the lever 288 and shaft 81 'counter clockWise against the action of a tension spring 30! attached to the lever so as to carry all of the 'zero stop levers 50 into blocking position relative to the zero locating ears 5! on the gears 85. Thus, as the machine continues its cycle, the racks [9 will be driven forward, rotating the gears 85 in a subtractive direction the opposite ends until they are stopped in their zero posi-' tions by the levers 50. The racks will therefore stand in positions mechanically representing the total values previously registered by the accumu lator whereby to cause the printing mechanism to register and print this value.

If desired numbered dials may be attached or geared in any suitable manner to the gears 85 so that amounts registered thereby may be visibly indicated.

Having thus described one embodiment of the invention, what I desire to secure by Letters Patent g 1. In a calculating machine having a plurality of rotatable accumulator elements of different denominational orders and means for driving said elements; tens transfer mechanism comprising the combination of a transfer actuator for each 'of said elements. said actuator having a driving tooth thereon, means for moving said actuator through a transferring stroke, means for normally guiding said actuator in a path wherein said tooth is ineffective to drive said element dur-= ing said stroke, means actuated by one of said elements upon movement thereof between nine and zero registration for conditioning the actua tor associated with the next higher order element to cause said tooth thereof to drive said next higher order element one increment during said stroke thereof, and a second tooth carried by said last mentioned actuator for engaging said next higher order element to positively prevent overthrow thereof beyond said increment.

2. In a calculating machine having a plurality of rotatable accumulator elements of different denominational orders and means for driving said elements; tens transfer mechanism comprising the combination of a transfer actuator for each of said elements, an element driving tooth on said actuator, means for moving said actuator through a transferring stroke,- said actuator being arranged to move selectively in a path wherein said tooth is ineffective to drive said element and in a second path wherein said tooth is effective to drive said element during said stroke, means for guiding said acuator in either of said two paths, means impelled by one of said elements upon movement thereof between nine and zero registration for locating the actuator associated with the next higher order element in said second path whereby to drive the same during said stroke, and a second tooth on each of said actuators adapted to engage its associated element upon movement of its respective actuator through said strokewhereby to prevent overthrow of said associated element;

3. In a calculating machine having a plurality or rotatable toothed accumulator elements of different denominational orders and means for driv' ing said elements; tens transfer mechanism comprising the combination of a transfer actuator for each of said element's, means for moving said actuator through a transferring stroke, means forming a pivotal connection between said actuator and said moving means, locating means for alternatively maintaining said actuator in one rocked position about said pivotal connection wherein said actuator misses said element during said stroke and for maintaining said actuator in a second rocked position wherein said actuator engages a tooth or said element whereby to drive the same during said stroke, means actuated by the next lower order element on movement there'- of between nine and zero registration for moving said last mentioned actuator into said second rocked position, and means comprising a second tooth on said last mentioned element operable during said driving movement of its associated actuator to move the latter into its said first mentioned rocked position.

'4. In a calculating machine having a plurality of rotatable accumulator elements of different denominational orders and means for driving said elements; tens transfer mechanism comprising the combination of a transfer actuator for each of said elements, said actuator having two teeth thereon, means for moving said actuator through a transferring stroke, means for normally guiding said actuator in a path wherein said teeth miss said element during said stroke, and means actuated by one of said elements upon movement thereof from nine to zero registration for conditioning the actuator associated with the next higher order element to cause one of said teeth to drive the same one increment in one direction during "said stroke, said conditioning means being actuated by said one element upon movement thereof from zero to nine registration for conditioning said last mentioned actuator to cause the other or said teeth to drive said next higher order element one increment in anopposite direction,

both. of said teeth being Operable substantially at the end of said transfer stroke to positively prevent overthrow and rebound of said element beyond said increment.

5. In a calculating machine having a plurality of rotatable accumulator elements of different denominational orders and means for driving said elements; tens transfer mechanism comprising' the combination of a transfer actuator for each of said elements, means for moving said actuator through a transferring stroke, means on said actuator forming a pair of driving teeth, means normally uiuingsaiu actuator in a path wherein said teeth are mefiective to drive Said. e'le'rnent during said stroke, and means actuated bi? one; of said elements on movement thereof from nine to zero registration tocondition the actuator associated with the next higher order element to cause one of said teeth thereof to drive said higher order "element one increment in one direction during said stroke, said last nie'ntioned means bein adapted to be actuated by said one element on movement thereof from zero to nine registration to condition the actuator associated with said next higher order element to cause the other of said teeth thereof to drive said next higher order element on increment in the opposite direction during said stroke, said next higher order element being operable during said driving movement of its associated actuator to condition the latter to engage both of said teeth thereof with said last '11 mentioned element whereby to prevent overthrow thereof beyond said increment.

6. In a calculating machine having a plurality of rotatable accumulator elements of different denominational orders and means for driving said elements; tens transfer mechanism comprising the combination of a transfer actuator for each of said elements, means on said actuator forming a pair of driving teeth, a pair of swinging levers pivotally supporting said actuator and arranged to swing in substantially parallel relationship to guide said actuator through a transferring stroke, means for moving said actuator through said transferring stroke, said levers being normally eifective to guide said actuator in a path wherein said teeth are ineffective to drive said element, and means actuated by one of said elements upon movement thereof between nine and zero registration for arranging the pivotal connection between the actuator associated with the next higher order element and one of said supporting levers therefor to guide said last mentioned actuator in a path wherein one of said teeth thereof drives said last mentioned element one increment in one direction during said stroke, said arranging means being adapted to be actuated by said one element upon movement thereof from zero to nine registration to arrange said pivotal connection to guide said last mentioned actuator in a path wherein the other of said teeth thereof drives said last mentioned element one increment in the opposite direction, said last mentioned element being effective during driving movement of said actuator to arrange said pivotal connection to cause said actuator to engage both of said teeth thereof with said last mentioned element whereby to prevent overthrow thereof beyond said increment.

7. In a calculating machine having a plurality of rotatable accumulator elements of different denominational orders and means for driving said elements; tens transfer mechanism comprising the combination of a transfer actuator for each of said elements, means on said actuator forming a pair of driving teeth, a pair of swinging levers pivotally supporting said actuator and arranged to swing in substantially parallel relationship to guide said actuator through a transferring stroke, means for moving said actuator through said transferring stroke, said levers being normally effective to guide said actuator in a path wherein said teeth are ineffective to drive said element, means actuated by one of said elements upon movement thereof between nine and zero registration for arranging the pivotal connection between the actuator associated with the next higher order element and one of said supporting levers therefor to guide said last mentioned actuator in a path wherein one of said teeth thereof drives said higher order element one increment in one direction during said stroke, said arranging means being adapted to be actuated by said one element upon movement thereof from zero to nine registration to arrange-said pivotal connection to guide said last mentioned actuator in a path wherein the other of said teeth thereof drives said higher order element one increment in the opposite direction and means for moving said last mentioned actuator into a position wherein both of said teeth thereof engage said higher order element whereby to prevent overthrow of said higher order element beyond said increment.

8. In a calculating machine having a plurality of accumulator gears of different denominational orders and means for driving said gears; tens transfer mechanism comprising the combination of a transfer actuator for each of said gears, means on said actuator forming a pair of driving teeth for driving said gear, means comprising a swinging lever pivotally connected to said actuator at one side of said gear for reciprocating said actuator through a transferring stroke; means for guiding said actuator through a path wherein said teeth are ineffective to drive said gear during said stroke, said guiding means comprising a second swinging lever movable in substantially parallel relation to said first mentioned lever, and means forming a second pivotal connection between said actuator and said second lever at the opposite side of said gear; and means actuated by one of said gears upon movement thereof from nine to zero registration to arrange the pivotal connection between the actuator associated with the next higher order gear and said second lever associated therewith to guide said last mentioned actuator in a path wherein one of said teeth thereof drives said next higher order gear one increment in an additive direction, said arranging means being adapted to be actuated by said one gear upon movement thereof from zero to nine registration to arrange said last mentioned actuator in a path wherein the other of said teeth thereof drives said next higher order gear one increment in a subtractive direction, said next higher order gear being effective during driving movement of said last mentioned actuator to arrange said last mentioned pivotal connection thereof to cause said last mentioned actuator to engage both of said teeth thereof with said next higher order gear whereby to prevent overthrow thereof beyond said increment.

9. In a calculating machine having a plurality of rotatable accumulator elements of different denominational orders and means for driving said elements; tens transfer mechanism comprising a transfer actuator for each of said elements, means on said actuator forming a pair of driving teeth, means for moving said actuator through a transferring stroke, means for normally retaining said actuator in an ineffective condition during said movement thereof, and means responsive to movement of one of said elements, when a tens transfer is indicated, for rendering the actuator associated with the next higher order element effective to cause one of said teeth to drive said higher order element, means on each of said elements for returning its associated actuator to ineffective condition during said movement thereof while in effective condition, both of said teeth being effective to positively lock the associated element against rebound and overthrow during the last portion of said'movement thereof.

EDWARD P. DRAKE.

REFERENCES CITED The following references are of record in the 153,237 Great Britain Nov. 4, 1920 

